Axial-flow fan unit and heat-emitting element cooling apparatus

ABSTRACT

An axial-flow fan unit that produces less noise is provided. Blades  19  are exposed from a venturi  29 . The shape of each of the blades  19  is so defined that a space formed between at least an inner surface  28   a  of each of web leg sections  28 A to  28 C and an edge  19   a  of each of the blades  19  located in the radially outward direction of the blades  19  expands toward the ends of the web leg sections  28 A to  28 C (or web bodies  30 A to  30 C). With this arrangement, noise produced when the blades  19  rotate along the web leg sections  28 A to  28 C is reduced.

BACKGROUND OF THE INVENTION

The present invention relates to an axial-flow fan unit and aheat-emitting element cooling apparatus which uses the axial-flow fanunit, for cooling a heat emitting element such as an electroniccomponent.

Such a heat-emitting element cooling apparatus has been know thatincludes a heat sink having a base and a plurality of radiation fins,and a fan unit. In this apparatus, a heat-emitting element to be cooledis mounted on the rear surface of the base, and the plurality ofradiation fins are fixed to the base. The fan unit is disposed above theheat sink, for blowing air along at least the radiation fins to promoteheat dissipation from the radiation fins. In this heat-emitting elementcooling apparatus, heat generated from the heat-emitting element istransferred from the base to the radiation fins. Then, the air flowingfrom the fan unit along the radiation fins carries away the heat of theradiation fins, thereby cooling the heat-emitting element.

U.S. Pat. No. 6,407,913 discloses an electronic component coolingapparatus where a heat sink provided with a plurality of radiation finsjuxtaposed on a base, is cooled by a fan unit.

Japanese Patent Application No. 267093/2002 (Laid-Open Publication No.104020/2004), which is the prior application of the applicant of thepresent invention, discloses an axial-flow fan unit in which the shapeof a venturi is so defined that, as seen from the radially outwarddirection of the revolving shaft of a motor for rotating an impeller,part of a plurality of blades located on the side of the motor can beseen.

Further, U.S. Design Pat. No. 441,724 and U.S. Design Pat. No. 450,306disclose a heat sink constituted by a radiation group comprising fourspace-dividing radiation fins and a plurality of subdividing radiationfins. In this heat sink, the four space-dividing radiation fins directlyextend from the outer periphery of a base in the radial direction of therevolving shaft of a motor, thereby dividing a space surrounding theouter periphery of the base into four spaces. The plurality ofsubdividing radiation fins are located within the divided spaces inorder to further subdivide the divided spaces. A part of the subdividingradiation fins respectively extend outward from two of thespace-dividing radiation fins adjacent to each other, and the remainingsubdividing radiation fins respectively extend outward from the outerperiphery of the base located between two adjacent space-dividingradiation fins.

Like the axial-flow fan unit as shown in Japanese Patent Application No.267093/2002 (Laid-Open Publication No. 104020/2004), in which the shapeof the venturi is so defined that part of a plurality of blades locatedon the side of the motor can be seen as viewed from the radially outwarddirection of the revolving shaft of the motor for rotating the impeller,comparatively large noise might be produced.

SUMMARY OF THE INVENTION

Accordingly, an object of the present invention is to provide anaxial-flow fan unit that produces less noise.

Another object of the present invention is to provide a heat-emittingelement cooling apparatus that has high cooling performance and alsoproduces less noise.

An axial-flow fan unit of which the present invention aims atimprovement includes: a motor having a revolving shaft; an impellerhaving a plurality of blades and mounted on the revolving shaft; acylindrical venturi surrounding the impeller in the radial direction ofthe revolving shaft; and a plurality of webs spaced in the radialdirection, for connecting the venturi to the housing of the motor. Then,the shape of the venturi is so defined that part of the blades locatedon the side of the housing of the motor can be seen, as viewed from theradially outward direction. Further, each of the webs includes: a webleg section extending from the end of the venturi toward a side of thehousing of the motor and having an inner surface continuous with theinner periphery surface of the venturi; and a web body located betweenthe housing and the end of the web leg section on the side of thehousing. Then, the axial-flow fan unit draws in air from the side of themotor and blows the air into the venturi.

In the axial-flow fan unit according to the present invention, the shapeof each of the blades is so defined that a space formed between at leastthe inner surface of the web leg section and the edge of each of theblades located in the radially outward direction expands toward the endof the web leg section.

Incidentally, the space between the inner periphery surface of theventuri and the edge of each of the blades may be fixed. Then, theshapes of the blades may be so defined that a space formed among theinner periphery surface of the venturi, the inner surface, and the edgeof each of the blades located in the radially outward direction expandstoward the end of the web leg section.

In other words, the space is gradually expanding toward the end of theweb leg section (or each of the web bodies) so as to reduce the noiseproduced when the edge of each of the blades moves along the innersurface of the web leg section.

According to the present invention, the noise produced when the bladesrotates along the web leg sections with part of the blades protrudingfrom the venturi can be greatly reduced. If the space is expanded toomuch, the volume of airflow is also reduced though the noise isdecreased. On the contrary, if the space does not expand enough, thevolume of the airflow is not reduced, but a reduction in noise becomesless. Thus, an increase in space expansion should be determined asnecessary, based on the required volume of airflow and the desiredreduction in noise. The reason why the noise is reduced is uncertain.However, actual tests have confirmed that the noise is reduced.According to the result of the tests, it is preferable that the shapesof the blades are so defined that an angle between the edge of eachblade and an inner surface of a virtual cylinder, with which a radiallyoutermost vertex of the edge of each blade is inscribed, becomesapproximately 4° or more. If the angle is in this range, the noise canbe reduced without substantially decreasing the volume of the airflow.Preferably, the major parts of the respective edges of the blades areformed to be inscribed in a common virtual cone. Generally, the edges ofthe blades on the side of the housing have arcs (curvatures). It isconsidered that the curvature of the arcs does not significantly affectthe reduction of the noise so much.

Preferably, the inner surface of the web leg section is continuous withthe inner periphery surface of the venturi and is curved along the innerperiphery surface. In this case, the curvature of the inner surfacebecomes substantially the same as that of the inner periphery surface ofthe venturi. With this arrangement, a reduction in noise with respect toan increase in space expansion can be increased.

A heat-emitting element cooling apparatus of which the present inventionaims at improvement includes: a heat sink including a base with aheat-emitting element to be cooled mounted on a rear surface thereof anda heat radiation fin group constituted by a plurality of radiation fins,fixed to the base; and an axial-flow fan unit arranged above the heatsink, for blowing air along at least the radiation fins constituting theradiation fin group to promote heat dissipation from the radiation fins.Then, the base of the heat sink has a columnar shape. Further, theradiation fins are disposed outside the base in a radial direction ofthe base. More specifically, the radiation fins are directly orindirectly fixed to the columnar base, and extend both in the radiallyoutward direction of the base and the height direction of the outerperiphery surface of the base or the direction extending from the fanunit to the heat sink. A preferred fan unit is the axial-flow fan unitof the present invention.

The radiation fin group in the heat sink can be constituted by: two ormore space-dividing radiation fins directly extending from the outerperiphery of the base in the radially outward direction, for dividing aspace surrounding the outer periphery of the base into a plurality ofdivided spaces; and a plurality of subdividing radiation fins locatedwithin the divided spaces. A part of the subdividing radiation finsrespectively extend outward from two of the space-dividing radiationfins adjacent to each other and the remaining subdividing radiation finsrespectively extend outward from the outer periphery of the basearranged between two adjacent space-dividing radiation fins so that thedivided spaces are further subdivided. With this arrangement, comparedwith the case where the radiation fins are radially arranged withrespect to the base, the total surface area of the radiation fins can beincreased. For this reason, the cooling performance of the apparatus canbe improved.

Preferably, the subdividing radiation fins located within each of saiddivided spaces are inclined in a direction opposite to the rotatingdirection of the impeller. With this arrangement, the cooling effect ofthe apparatus can be enhanced. Though the reason for this is not clear,it is considered that the cooling effect can be enhanced because coolingairflow efficiently strikes the fins.

Preferably, the shapes of the two or more space dividing radiation finsmay be so defined that enough heat dissipation can be performed throughthe subdividing radiation fins joined to the respective space dividingradiation fins.

According to the present invention, the noise produced when the bladesrotate along the web leg sections with part of the blades protrudingfrom the venturi can be greatly reduced.

BRIEF DESCRIPTION OF THE DRAWINGS

These and other objects and many of the attendant advantages of thepresent invention will be readily appreciated as the same becomes betterunderstood by reference to the following detailed description whenconsidered in connection with the accompanying drawings; wherein:

FIG. 1 is a top plan view of a heat-emitting element cooling apparatusaccording to an embodiment of the present invention, applied to anelectronic component cooling apparatus;

FIG. 2 is a right-side elevation view of the heat-emitting elementcooling apparatus according to the embodiment of the present invention,applied to the electronic component cooling apparatus;

FIG. 3 is a front elevation view of the heat-emitting element coolingapparatus according to the embodiment of the present invention, appliedto the electronic component cooling apparatus;

FIG. 4 is a bottom plan view of the heat-emitting element coolingapparatus according to the embodiment of the present invention, appliedto the electronic component cooling apparatus;

FIG. 5 is a perspective view of the electronic component coolingapparatus;

FIG. 6 is a perspective view of a heat sink of the electronic componentcooling apparatus;

FIG. 7(A) is a front view of an impeller used in the electroniccomponent cooling apparatus;

FIG. 7(B) is a plan view, partially broken away, of the impeller used inthe electronic component cooling apparatus; and

FIG. 7(C) is a rear view of the impeller used in the electroniccomponent cooling apparatus.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENT

FIGS. 1 to 4 are respectively a top plan view, a right-side elevationview, a front elevation view, and a bottom plan view of a heat-emittingelement cooling apparatus according to an embodiment of the presentinvention, which is applied to an electronic component coolingapparatus. FIG. 5 is a perspective view of an electronic componentcooling apparatus 1 illustrated in FIGS. 1 to 4. FIG. 6 is a perspectiveview of a heat sink 3 used in the electronic component coolingapparatus. FIGS. 7(A) to 7(C) are respectively a front view, a planview, partially broken away, and a rear view of an impeller used in theelectronic component cooling apparatus. As shown in these drawings, theelectronic component cooling apparatus 1 in this embodiment includes theheat sink 3 and an axial-flow fan unit 5. As illustrated in FIG. 4, theheat sink 3 includes a base 7 and a radiation fin group 9 fixed to thebase 7. The base 7 is constituted by a cylindrical hollowed centralsection 7 a including a cavity in its inside and a high thermalconductor 7 b. The high thermal conductor 7 b is arranged within thecavity so that it can conduct heat to the cylindrical hollowed centralsection 7 a and has a thermal conductivity higher than that of amaterial employed for forming the hollowed central section 7 a. The highthermal conductor 7 b is formed of copper having a thermal conductivityhigher than the thermal conductivity of the material (i.e. aluminum) forthe radiation fin group 9 and the hollowed central section 7 a, and hassubstantially a cylindrical shape. The diameter of the base 7 (outerdimensions of the hollowed central section 7 a) is equal to or less thanthe outer dimensions of an impeller 23 of the axial-flow fan unit 5described hereinafter.

As illustrated in FIG. 4, the radiation fin group 9 is fixed to theouter periphery of the base 7. A heat-emitting element constituted by anelectronic component to be cooled is mounted on the rear surface of thebase 7 or a bottom surface 7 c opposite to the side where the axial-flowfan unit 5 is located. This heat sink 3 is so constructed that all ofradiation fins 13A to 13D and 15 of the radiation fin group 9 arelocated outside the contour of the base 7 or the cylindrical hollowedcentral section 7 a, as seen from the side where the axial-flow fan unit5 is disposed.

The radiation fin group 9 is constituted by four space-dividingradiation fins 13A to 13D integrally fixed to the cylindrical hollowedcentral section 7 a and the subdividing radiation fins 15 fixed to thehollowed central section 7 a and the space-dividing radiation fins 13Ato 13D. Referring to FIGS. 4 and 6, the structure of the radiation fingroup 9 will be described. Each of the four space-dividing radiationfins 13A to 13D includes a plate-like fin body 13 a fixed to thehollowed central section 7 a, a first plate-like portion 13 b fixed tothe tip of the fin body 13 a, and a second plate-like portion 13 c fixedto the tip of the first plate-like portion 13 b. The fin body 13 a has ashape of which the thickness or dimension in the peripheral direction ofthe hollowed central section 7 a gradually decreases from its baseintegrally fixed to the hollowed central section 7 a to its tip or inthe radially outward direction of the hollowed central section 7 a. Thisshape is so defined that enough heat dissipation can be performedthrough the subdividing radiation fins 15. The first plate-like portion13 b and the second plate-like portion 13 c are so arranged that thecross section or the shape of them as seen from the rear surface of theheat sink 3 is of an L shape. Further, the four space-dividing radiationfins 13A to 13D are so arranged that the second plate-like portion 13 cof the space-dividing radiation fin 13A is parallel to the secondplate-like portion 13 c of the space-dividing radiation fin 13D, andthat the second plate-like portion 13 c of the space-dividing radiationfin 13B is parallel to the second plate-like portion 13 c of thespace-dividing radiation fin 13C. As illustrated in FIG. 3 and FIG. 6,each of the second plate-like portion 13 c has a lower end surface 13 d.These lower end surfaces 13 d constitute engaged sections to be engagedwith engagement pieces 35 of a fan casing 25 described hereinafter.

The four space-dividing radiation fins 13A to 13D directly extendradially from the hollowed central section 7 a and then divides a spacesurrounding the outer periphery of the base 7 into four divided spacesS1 to S4. More specifically, the two space-dividing radiation fins 13Aand 13C are arranged at two locations mutually 180° apart in theperipheral direction of the base 7. Further, the two space-dividingradiation fins 13B and 13D are arranged at another two locationsmutually 180° apart in the peripheral direction of the base 7.

The subdividing radiation fins 15 are located within the divided spacesS1 to S4 for further subdividing the divided spaces S1 to S4. Thesubdividing radiation fins 15 located between the two adjacentspace-dividing radiation fins 13A and 13B, 13B and 13C, 13C and 13D, and13D and 13A extend outward from such two adjacent space-dividingradiation fins and the hollowed central section 7 a located between thetwo adjacent space-dividing radiation fins. A plurality of thesubdividing radiation fins 15 located within each of the divided spacesS1 to S4 are inclined in a direction opposite to the rotationaldirection of the impeller 23 described hereinafter, or the direction ofan arrow in FIG. 1. With this arrangement, the effect of cooling can beenhanced.

As illustrated in FIGS. 1 through 3 and FIG. 5, the axial-flow fan unit5 includes a motor 17, the impeller 23 having seven blades 19 and acup-like blade mounting section 21 (illustrated in FIG. 2) for beingdriven for rotation by the motor 17, the fan casing 25, and three webs27A to 27C. Then, the axial-flow fan unit 5 draws in air from the sidewhere the webs 27A to 27C are disposed, and operates to blow air towardthe radiation fin group 9. In this embodiment, the fan casing 25, ahousing 17 a of the motor 17, and the webs 27A to 27C are integrallyformed using a molding compound mainly made of a synthetic resinmaterial

In the axial-flow fan unit 5, the motor having a revolving shaft notshown is used as a driving source, and the impeller 23 mounted on therevolving shaft is rotated with respect to the revolving shaft. Theaxial-flow fan unit 5 is mounted on the heat sink 3 so that the rotationcenter of the revolving shaft is substantially aligned with the centerof the base 7 of the heat sink 3. In this embodiment, the outerdimensions of the base 7 (cylindrical hollowed central section 7 a) areset to be smaller than the outer dimensions of the blade mountingsection 21.

As illustrated in FIGS. 1 to 5 in detail, the fan casing 25 includes acylindrical venturi 29 for rotatably receiving the impeller 23, anopposite wall section 31 located outside the venturi 29 to face the heatsink 3, a peripheral wall section 33 provided at the opposite wallsection, which extends toward the base 7, and the four engagement pieces35 provided at the opposite wall section 31. As illustrated in FIGS. 2,3, and 5, the shape of the venturi 29 is so defined that part of theblades 19 located on the side of the housing 17 a of the motor 17 can beseen from the radially outward direction of the revolving shaft of themotor. In other words, since the dimension of the venturi 29 in its axisline direction is short, part of the blades 19 are exposed from oneopening end of the venturi 29. The venturi 29 has a first taper sectionat its opening end on the side of the housing of the motor 17, which iswidened in the radially outward direction of the revolving shaft of themotor, a straight line section with the same diameter size, continuouswith the first taper section, and a second taper section that is widenedin the radially outward direction, continuous with the straight linesection. Inner surfaces 28 a of web leg sections 28A to 28C describedhereinafter are continuous with the straight line section in an innerperiphery surface 29 a of the venturi 29.

As illustrated in FIG. 4, at the opposite wall section 31 of the fancasing 25, two spacer means 34 are arranged between the opposite wallsection 31 and the radiation fin group 9, for forming a space betweenthe opposite wall section 31 and the radiation fin group 9 and alsomaintaining the space.

As illustrated in FIGS. 3 and 4, the peripheral wall section 33 has afirst pair of side walls 33A facing part of the subdividing radiationfins 15 within the two divided spaces S1 and S3 described before in thelateral direction of the fan casing 25 and a second pair of side walls33B facing the subdividing radiation fins 15 within the two dividedspaces S2 and S4 in the lateral direction of the fan casing 25. Thefirst pair of side walls 33A are constituted by three side wall portions38 a, 38 b, and 38 c, which are divided by two slits 36. The two sidewall portions 38 a and 38 c on both sides are provided with hooks 38 d(illustrated in FIG. 2) for engaging with metal mountings not shown. Theslits 36 permit the side wall portions 38 a and 38 c to be inclinedinward when the side wall portions 38 a and 38 c are subject to anexternal force. The first pair of the side walls 33A and the second pairof side walls 33B form a space between the opposite wall section 31 andthe heat sink 3 for passing the air discharged from the impeller 23, andare arranged to prevent all or most part of the air that has passedthrough this space from being directly discharged to outside the fancasing 25 without passing through intervals among the subdividingradiation fins 15.

As illustrated in FIGS. 3 and 5, each of the four engagement pieces 35has a main body section 31 a that extends from the opposite wall section31 toward the heat sink 3 and an engagement projecting section 31 b thatprojects toward the base 7 from the edge of the main body section 31 aon the side of the heat sink 3. The engagement projecting sections (orhooks) 31 b of the four engagement pieces 35 are snap-in engaged withthe lower end surfaces 13 d in the second plate-like portions 13 c atthe tips of the space-dividing radiation fins 13A to 13D. In thismanner, the axial-flow fan unit 5 is detachably mounted on the heat sink3.

As illustrated in FIGS. 1 and 5, the three webs 27A to 27C are arrangedbetween the fan casing 25 and the motor 17, and then supports the motor17. The three webs 27A to 27C include web leg sections 28A to 28C andweb bodies 30A to 30C, respectively. Each of the web leg sections 28A to28C has the inner surface 28 a that extends from the end of the venturi29 to the housing 17 a of the motor 17 and is also continuous with theinner peripheral surface 29 a of the venturi 29. The web bodies 30A to30C are located between the housing 17 a and the ends of the web legsections 28A to 28C, respectively.

In this axial-flow fan unit 5, the shape of each of the blades 19 is sodefined that a space S formed between at least the inner surface 28 a ofeach of the web leg sections 28A to 28C and an edge 19 a located in theradially outward direction of each of the blades 19 expands toward theends of the web leg sections 28A to 28C (or web bodies 30A to 30C). Withthis arrangement, noise produced when the blades 19 rotate along the webleg sections 28A to 28C, with part of the blades 19 protruding from theventuri 29, can be greatly reduced.

Incidentally, the space between the inner periphery surface 29 a of theventuri 29 and the edge 19 a of each of the blades 19 may be fixed.Then, the shape of each of the blades 19 may be so defined that thespace formed among the inner surface 28 a of each of the web legsections 28A to 28C, the inner periphery surface 29 a of the venturi 29,and the edge 19 a located in the radially outward direction of each ofthe blades 19 expands toward the ends of the web leg sections 28A to28C. In other words, in order to reduce the noise produced when theedges 19 a of the blades 19 move along the inner surfaces 29 a of theweb leg sections 28A to 28C, the space may expand gradually toward theends of the web leg sections 28A to 28C (or the web bodies).

In this embodiment, the inner surfaces 28 a of the web leg sections 28Ato 28C are continuous with the inner peripheral surface 29 a of theventuri 29 and are curved along the inner peripheral surface 29 a. As aresult, the curvature of the inner surfaces 28 a of the web leg sections28A to 28C becomes substantially the same as that of the innerperipheral surface 29 a of the venturi 29. With this arrangement, areduction of the noise with respect to an increase in space expansiondescribed before can be increased.

The shape of the impeller 23 for forming the above-mentioned space is asillustrated in FIG. 7. As illustrated in FIG. 7(A) and 7(C), it ispreferable that the shapes of the blades are so defined that an angle θbetween the edge 19 a and an inner surface IS of a virtual cylinder FC,with which the outermost vertices in the radial direction of the edges19 a of the blades 19 are inscribed, becomes approximately 4° or more.In this embodiment, the major parts of the respective edges 19 a of theblades 19 are inscribed in a common virtual cone located inside thevirtual cylinder FC having the inner surface IS. Thus the angle θ canalso be defined to be the angle formed between the inner surface IS ofthe virtual cylinder FC and the virtual cone surface. Though this angleθ may vary depending on the shapes of the respective blades, when thisangle θ is within a range of 4°+−0.5°, for example, a preferable resultof noise reduction can be obtained. However, the proper range of theangle θ may vary depending on the shapes of surrounding members, theshape and dimensions of the blades, and the rotational speed of themotor. Therefore, the proper range cannot necessarily be determined atthe present stage. Nevertheless, it is confirmed by experiment that, bydetermining the angle θ as necessary, the noise can be reduced withoutsubstantially reducing the volume of the airflow delivered from the fanunit. An arrow F in FIG. 7(B) indicates the direction of the airflowwhile the impeller 23 is rotating.

As illustrated FIG. 7, arcs (curvatures) are formed at the ends on bothsides of the edge 19 a in each of the blades 19 in the axial linedirection of the blades. Tests were conducted on the effect of an arc(curvature) 19 b located on the side of the housing 17 a of the motor 17in particular. Regardless of whether the curvature radius of the arc(curvature) 19 b is large or small, reduction of the noise was notgreatly affected. However, in regard to the arc (curvature) 19 b, alarger curvature radius of the arc is considered to more contribute tothe noise reduction than a smaller curvature radius of the arc.

Out of the webs 27A to 27C, electrical wires 39 for supplying power tothe motor 17 are arranged inside the web 27A. Further, as illustrated inFIG. 1, the web bodies 30A to 30C of the three webs 27A to 27C,respectively, extend in the tangent direction of the revolving shaftrather than in the radial direction of the revolving shaft.

Further, the present invention is not limited to this embodiment, butvarious variations and modifications may be made without departing fromthe scope of the present invention.

1. An axial-flow fan unit comprising: a motor having a revolving shaft;an impeller having a plurality of blades and mounted on said revolvingshaft; a cylindrical venturi surrounding said impeller in a radialdirection of said revolving shaft; and a plurality of webs spaced in acircumferential direction of said revolving shaft, for connecting saidventuri to a housing of said motor; a shape of said venturi being sodefined that part of said blades located on a side of said housing ofsaid motor can be seen as viewed from the radially outward direction;each of said webs comprising: a web leg section extending from an end ofsaid venturi toward a side of said housing of said motor; and a web bodylocated between said housing and an end of said web leg section on theside of said housing; said web leg section having an inner surfacecontinuous with an inner periphery surface of said venturi; and saidaxial-flow fan unit drawing in air from a side of said motor and blowingthe air into said venturi; wherein a shape of each of said blades is sodefined that a space formed between at least said inner surface of saidweb leg section and an edge of each of said blades located in theradially outward direction expands toward said end of said web legsection.
 2. The axial-flow fan unit according to claim 1, wherein saidspace gradually expands toward said end of said web leg section so as toreduce noise produced when said edge of each of said blades moves alongsaid inner surface of said web leg section.
 3. The axial-flow fan unitaccording to claim 1, wherein shapes of said blades are so defined thatan angle between said edge and an inner surface of a virtual cylinder,with which a radially outermost vertex of said edge of each of saidblades is inscribed, becomes approximately 4° or more.
 4. An axial-flowfan unit comprising: a motor having a revolving shaft; an impellerhaving a plurality of blades and mounted on said revolving shaft; acylindrical venturi surrounding said impeller in a radial direction ofsaid revolving shaft; and a plurality of webs spaced in acircumferential direction of said revolving shaft, for connecting saidventuri to a housing of said motor; a shape of said venturi being sodefined that part of said blades located on a side of said housing ofsaid motor can be seen as viewed from the radially outward direction;each of said webs comprising: a web leg section extending from an end ofsaid venturi toward a side of said housing of said motor; and a web bodylocated between said housing and an end of said web leg section on theside of said housing; said web leg section having an inner surfacecontinuous with an inner periphery surface of said venturi and curvedalong said inner periphery surface; and a shape of each of said bladesbeing so defined that a space formed among said inner periphery surface,said inner surface, and an edge of each of said blades located in theradially outward direction expands toward said end of said web legsection.
 5. The axial-flow fan unit according to claim 4, wherein saidspace gradually expands toward said end of said web leg section so as toreduce noise produced when said edge of each of said blades moves alongsaid inner surface of said web leg section.
 6. The axial-flow fan unitaccording to claim 4, wherein shapes of said blades are so defined thatan angle between said edge and an inner surface of a virtual cylinder,with which a radially outermost vertex of said edge of each of saidblades is inscribed, becomes approximately 4° or more.